Fluid lift system



Oct. 27, 1964 M. H. wlLLlTs 3,154,018

FLUID LIFT SYSTEM Filed April 2, 1962 7 sheets-sheet 1 MM, a, M *@L- hisATTORNEYS OCt- 27 1964 M. H. wlLLlTs 3,154,018

FLUID LIFT SYSTEM l Hl Filed April 2, 1962 '7 Sheets-Sheet 2 g i? l 204/ P32@ +5 1 Ck Ck 29 42 Q 42 im 43 5 ,if

F/ae 58 49,- .49 kg/9 Q 14? 35' 24 l fa 8 57 24 1 I his ATTORNEYS Oct.27, 1964 M. H. wlLLlTs FLUID LIFT SYSTEM Oct. 27, 1964 M. H. wlLLlTs3,154,018

FLUID LIFT SYSTEM VALVES I4, 27, 28, 29 8i 30 operate as a function ofthe PRESSURE within casing area 33. VALVES 94a 8i 94b operate as ofunction of the DISPLACEMENT of barrel 26.

VALVES 3| 8i 32 operate as a function of the PRESSURE DIFFERENTIALbetween barrel 26 and tubing 20.

r= normal rate at which pressure increases in the sealed system due topump IO.

r30= rate of pressure increase with valve 30 open to production tubing20.

I'- 28= rate of pressure increase with Valve 28 open to productiontubing 20.

INVENTOR. MYRON H. WILLITS 4 817W/ @al his ATORNEYS Oct. 27, 1964 M. H.wlLLlTs FLUID LIFT SYSTEM '7 Sheets-Sheet 6 Filed April 2, 1962 INVENIIIIL lill..

. h .1. MmuhbwmwwwhwnNUN. 7

Torn MYRON H. WILLITS BY Z l2 ,a a

his Arron/vers Oct. 27, 1964 M. H. WILLI-rs FLUID LIFT SYSTEM '7Sheets-Sheet 7 Filed April 2, 1962 mm NM ww mH. N O R Y M Miam/M fw hisATTR/VEYS United States Patent O 3,154,018 FLUEE LEFT SYSTEM Myron H.Willits, 1331 New York St., New tlrleans, La.,

assigner ot one and one-fourth percent to Leonard Glade and sixteen andone-fourth percent to icero C.

Sessions, both ot New Grleans, La.

Filed Apr. 2, 1962, Ser. No. 184,245 21 Claims. (Cl. 10S- 45) Thisinvention relates to systems for obtaining tluids from distant orrelatively inaccesible locations and, more particularly, to a systemthat moves fluids through a closed conduit by the proper application ofhydrostatic pressures.

This application is a continuation-in-part of my cepending applicationSerial No. 29,902, filed on May 18, 1960 for a Fluid Lift System nowabandoned.

There has long been a need for an apparatus that can draw largequantities of a fluid from inaccessible locations in an economicalmanner. This is especially true, for example, in the oil industry whereoil must be pumped from the wells after the natural pressures are nolonger sulllcient to lift it to the surface.

Present day pumping mechanisms for this purpose have severaldisadvantages, among them being those of depth and volume limitations.Usually the pumps are actuated by long sucker rods which extend to thesurface of the earth. In another type of system, a downhole pump isactuated by the flow of iluid that is pumped through it. Besides thefact that these installations are very expensive, they are difficult tomaintain and they cannot pump sizable quantities of lluid from greatdepths.

Accordingly, it is a purpose of the present invention to provide asystem for obtaining iluids such as oil from relatively inaccessiblelocations which does not have the above-described disadvantages. In apreferred embodiment of the invention, this system includes a lluidpressure operated pump adapted to be disposed in a borehole traversingsubterranean formations for obtaining well eflluent. This pump isconnected by a column of power transmission fluid to a system atsubstantially the surface of the earth for applying a variable pressureto the column.

The lluid pressure operated pump includes a traveling container, meansfor guiding the movement of the container, and a plurality of pressureoperated valves which are adapted to permit the power transmission fluidto exert pressure ilrst on one side of the traveling container when thepressure on the power transmission tluid is at a rst magnitude, and thenon its opposite side when the pressure on the power transmission fluidis increased to a second magnitude. By periodically changing thepressure on the column of power transmission iluid, the travelingcontainer is made to move back and forth. Further valves are providedwhich operate such that the container is periodically lllled and emptiedof the oil, which is pumped out of the well by the movement of thecontainer.

It can be seen that this system has considerable advantages becausepower is transmitted from the surface of the earth to the pump in thewell through a column of tluid on which pressure is periodicallyincreased and decreased. This is advantageous because mechanicallinkages are not needed, only one conduit is required in addition to thewell casing, and large quantities of the power transmission lluid arenot mixed with the lluid being pumped.

This invention can be more completely understood from the followingdetailed description taken in conjunction with the accompanying gures ofthe drawings in which:

FIG. 1 is a schematic diagram of a lluid lift system constructed inaccordance with the invention;

FIG. 2 is a general schematic representation in longi- Patented ct. 27,1964 ICC tudinal cross-section of an exemplary embodiment of a pump forthe system with its traveling barrel in a lirst position, in accordancewith the invention;

FlG. 3 is a schematic representation of the pump of FIG. 2 with itstravelingy barrel in a second position;

FIG. 4 is a graphical representation of a profile of the pressureexerted on the power transmission lluid during one cycle of operation ofthe system in response to one specic and exemplary valve sequence whichincorporates optional breaking valves.

FIGS. 56 are detailed cross-sectional elevations of exemplaryembodiments of valves that are adapted to be used with the system;

FIG. 7 is generally a side elevation in longitudinal cross-section of amore detailed configuration of the lower portion of a pump in the systemshowing the relative positions of the valves and the pump conduits, inwhich some of the construction details have been altered in order toclarify the illustration;

FIGS. 7A, 7B, 7C and 7D present detailed crosssectional views takenalong the lines 7A, 7B, 7C and 7D in FIG. 7 looking in the direction ofthe arrows;

FIG. 8 is a side elevation in longitudinal cross-section of a moredetailed configuration of the central portion of a pump in the systemwith its traveling barrel approaching the upper position;

FIG. 9 is generally a side elevation in longitudinal cross-section of amore detailed configuration of the upper portion of a pump in the systemshowing the relative positions of the valves and the pump conduits, inwhich some of the construction details have been altered in order toclarify the illustration; and

FIGS. 9A, 9B, 9C and 9D present detailed crosssectional views takenalong the lines 9A, 9B, 9C and 9D in FIG. 9 looking in the direction ofthe arrows.

The system illustrated in FIG. 1 includes a pump 10 at the earthssurface which is driven by a prime mover 11 and pumps a powertransmission lluid out of a reservoir 12 into a conduit 17. This lluidis forced under pressure through three valves 13, 14 and 15, comprisinga valve manifold, by the pump 10 to a well casing 16. The valves 13 and14 are conventional three-way valves, the valve 14 being adapted to openand allow fluid flow from the pump 10 to the well casing 16 at a lirstpressure in the conduit 17 and to prevent such tluid ilow at a secondpressure. When the valve 14 is operated to prevent flow from the pump 10to the casing 16, it provides a pressure relief path from the conduit 17to the conduit 18 through the valve 15, which is a one way check valve.The valve 13 is preferably coupled to the valve 14 in such a manner thatit passes fluid to the casing 16 only when the valve 14 is open anddirects the lluid to a bypass line 18 when the valve 14 is closed. Thevalve 1S, for example, a check valve, allows iluid to ilow only towardthe bypass line 13, which returns the power transmission tluid to thereservoir 12 when the valves 13 and 14 are closed.

A pump 19, to be described in detail hereinafter, is disposed within thewell casing 16 and forces oil upwardly through a production tubing 20and a flow line 21. This line may be connected, if required, to a heaterand separator unit 22 which separates the oil from the small quantity ofpower transmission iluid that is forced into the production tubing 20and from the natural gas accompanying the oil. The gas and oil are takenout of the unit 22 by suitable means and carried to conventional storagecontainers (not shown). The quantity of power transmission lluid istaken from the unit 22 by a return line 23 which returns it to thereservoir 12. In the event some of the power transmission lluid is lost,it may be replaced by a conduit 24 running to a supply pit, or, in thecase of excess lluid, the conduit 24 may be used to lead the lluid to adisposal pit.

The pump T19 in the well casing 16 is shown in detail in FIGS. 2 and 3.ln FlG. 2 the pump is at the beginning of a cycle and in FIG. 3 it is atapproximately the half-way point in its cycle. This pump is actuated bythe pressure exerted on it due to the power transmission fluid containedin area 33 between the well casing 16 and the outer wall of the pump i9,which is equal to the force on the column applied by the pump Il@ at thesurface of the ground and the weight of this column of Huid.

The pump 19 includes an outer mandrel 24 which is fastened to the lowerend of the tubing 2li. A conventional production packer 25 is used tocompletely seal off the section or the well casing le below the pumpfrom the section above the pump. The pump .T19 also includes a travelingcontainer or barrel 26 that moves between the down position shown inFIG. 2 and the up position shown in FIG. 3. Four pressure sensitivevalves 2?-3@ control the application of the pressure on the barrel 26,and consequently its movement, and two check valves 3l and 32 controlthe flow of oil into and out of the barrel.

The pressure applied on the column of iluid by pump l causes thepressure on pump i9 in the well to vary in accordance with the proleillustrated in FlG. 4 and the four valves 27-30 to operate according tothe schedule indicated. (It is to be noted that this profile and graphrepresent only one valve sequence for one particular embodiment. Theembodiment shown has incorporated braking valves which will be discussedlater and which are not incorporated in the embodiment shown in FIGS. 2and 3).

The valve 27 is a dual pressure operated type that is set to open at arst pressure and to close at a second higher pressure. When the pressureapplied on the column by pump lll at the surface of the ground isincreased from some low value to the point where the valve 27 opens, thepower transmission fluid passes from space 33, through valve 27 and intoa chamber 36 between a wall 3'7 and the outer wall 38 of the travelingbarrel 26 and lower wall 43 below lower member 4S as shown in FIGS. 2and 3.

The valve 3@ is also a dual pressure operated type. Its inlet port isconnected -to chamber 4Z and its outlet port to production tubing 2@ viachannel 4l. Valve 35.? is set to open only when the pressure in chamber42 reaches a predetermined value. Also this same valve closes when thepressure in chamber 4Z reaches a specic higher value. Upper chamber 42is similar to lower chamber 36 and is defined as the space withincylindrical wail 37 and external to cylindrical guide 43 and upper outerwall 38 of traveling barrel 26.

The valve 29 is a one-way pressure operated type that opens only whenthe pressure on the power transmission fluid within casing area 33 isabove a specic predetermined value, as indicated in FIG. 4. When valve29 is open, it allows the power transmission fluid within the casing-area 33, to flow through it into chamber 42. Valve 29 differs fromvalves 27 and 3@ in that it closes only when the pressure in area 33falls below its opening pressure as shown in FIG. 4.

The valve 2S is similar to valve 29 except that its inlet port isconnected to chamber 36 and its outlet port to production tubing Ztl viachannel 39 located within wall 24. Thus when the pressure within chamber36 reaches a predetermined value, valve 28 opens and remains open untilthe pressure in chamber 36 falls below this same predetermined value.

These four valves 274;@ are used in conjunction with a check mechanismthat permits uid through them in one direction only.

At the beginning of a cycle, the traveling barrel 26 is at the lowermostpoint in its travel and the check valve 31 is open, which allows theformation Huid to low through a suitable opening 44 of any desiredconfiguration in a plate 45 at the bottom of the pump into the travelingbarrel 26. The check valve 32 at the top of the pump is closed since thepressure exerted by the column of the well ellluent within productiontubing 20, which extends to the surface of the ground during operation,is greater than that within the traveling barrel 26. The four valves areinitially closed because the pressure ot the power transmission fluid atthe pump 19 is less than the predetermined opening pressures of thevalves.

When this pressure is increased to a predetermined level at an initialrate r due to the action of pump 1i? on a closed system as shown in FIG.4, the valve 27 opens and allows the power transmission iiuid to llowinto the chamber 36 within the pump. This liuid exerts an upwardlydirected force on the undersurface 46 of a member 47 formed on the outerwall 38 of the traveling barrel 26. This upward force on barrel 26correspondingly tries to compress the iluid within chamber 42. Due tothe relatively slight compressibility of the huid, the pressures in area33 :and chambers 36 and 4Z are soon equal and rising at rate r due tothe continued action of pump 1t). When the pressure in chamber 42reaches this initial predetermined level (or an optional higher level)valve Sil opens, allowing the power transmission uid in chamber 42 to beexhausted through valve 30 into production tubing 2t?. Since thepressure within production tube 20 is much less than 4the pressurewithin area 33 and chamber 36, the fluid within chamber 42 will befreely exhausted and barrel 26 will rise to the position shown in FIG.3. The rate ot pressure increase is, of course, less than r due to theloss of iluid through valve 30 and is designated r-B in FIG. 4.

The valve Si is located within the licor of traveling barrel 26. Thisvalve closes as it starts its upward motion and thereby compresses thewell effluent located within area 26. When the pressure within thebarrel 26 exceeds that within the production tubing 2li, valve 32 opensand allows the well eilluent to be forced from barrel 26 into theproduction tubing Ztl as the barrel proceeds upward to the positionshown in FIG. 3.

Seals 4d are fastened to the inner and outer walls of the barrel 26 insealing relation to the cylindrical guide member 43. Because of thefrictional losses inherent in the system and the throttling eiect aslluid escapes through valves Si) and 32, the pressure within area 33 andchamber 36 continues to increase as the traveling barrel 26 approachesthe upper limit of its displacement cycle. Finally in the detailedembodiment shown in FIG. 8, braking elements, which are discussed indetail below, equalize the pressure within casing area 33 and chambers42 and 36, thus removing the force acting on barrel 26 and allowing thefriction within the system to stop the barrels remaining inertia. Duringthis period the closing pressure of valve 27 is also reached.

ln a system without braking valves the pressure in casing area 33 wouldagain increase at the rate r after the closing of valve 27. However, asshown in FIG. 4, in a system with braking valves, the pressure continuesto ierease in casing area 33 at a rate r-30. In a system with brakingvalves, this pressure increase is also experienced within chamber 42,thereby allowing valve 30 to close once its higher closing pressure isreached but before valve 29 opens.

As the pressure exerted on the column of power transmission uid withinarea 33 is increased still further, due to the action of the pump at thesurface of the ground, the opening pressure for valve 2S? is reached.The power transmission fluid then enters chamber 4Z through the valve 29and exerts a downwardly directed force on the upper surface 49 of themember 47. In a system without braking valves, the pressure withinchamber 42 remains at the closing pressure of valve 27 until valve 29opens thereby keeping valve 3@ open. When valve 29 opens a much higherpressure enters chamber 42 which forces valve fr@ closed. Thus in asystem Without braking elements, valve 3@ closes only after valve 29opens even though the pressure in casing area 33 has previously exceeded its closing pressure.

Just before barrel 26 begins its downward movement, the pressures withincasing area 33 and in chambers 42 and 36 are equal and rising again atrate r. This soon exceeds the opening pressure of valve 23 which allowsthe power transmission fluid trapped in chamber 36 to escape therefrom,into the production tubing 26 via channel 39. Because the pressurewithin production tubing 26 is less than that in casing area 33 andchamber 42, the fluid within chamber 36 escapes freely, thereby allowingtraveling barrel 26 to proceed downwardly. The rate of pressure increaseis, of course, less than "r due to the loss of fluid through valve 28and is designated r-ZS in in FIG. 4.

As barrel 26 is forced downwardly, the pressure within barrel 26 is lessthan that within production tubing 26, thereby closing check valve 32.Meanwhile downwardly moving valve 3l opens and allows well ecluent tollow through the opening 44 in the plate 45 and to refill the travelingbarrel 26 prior to the next cycle.

To summarize, during each cycle the power transmission fluid enterschamber 36 below the member 47 and forces the traveling barrel 26upwardly; the uid in the chamber 42 on the other side of member 47 isdisplaced and flows through the valve 30 into the interior of theproduction tubing 26. Valve 27 closes as the traveling barrel 26 reachesthe top of its travel. Then as the pressure continues to increase, valve3@ closes and valve 29 opens, allowing the power transmission uid toenter chamber 42. This increased pressure forces member 47 and thetraveling barrel 26 downwardly as valve 23 opens, and the fluid on thelower side of the member 47 in chamber 36 is displaced and ilows throughthe valve 28 into the channel 39 and the interior of the productiontubing 26.

The pressure on the power transmission lluid,y required to drive thepump through this action is produced by the hydrostatic powertransmission lluid head in area 33 and the variable pressure produced bythe pump l@ at the surface of the ground which is controlled by thethree valves 13, 14, and l5. The pump l@ is preferably a type thatproduces a constantly increasing or decreasing flow such as acentrifugal pump rather than a piston type which produces a pulsatingow. The valve 14 is set to open and allow fluid to ilow from the pumplil to the well casing 16 when the pressure in the conduit 17 decreasesto a predetermined value and to close to this now when the pressure inthis conduit reaches a substantially higher predetermined value. Thecontrols on the valve t3 are preferably connected to the controls on thevalve i4 so that they open and close substantially simultaneously. Asexplained previously, when the valves i3 and 14 are closed, the fluidfrom pump lil is directed through valve 13 directly into conduit linei8; while at the same time the pressure previously built up with casingarea 33 is relieved as it tlows baci; through valve i4 and through checkvalve l5 into conduit line l, eventually reaching reservoir l2. lt canbe seen that the flow of the power transmission fluid from the pump lbis relatively constant although variable in magnitude from a lowpressure to a high pressure at a rate r and variable from a highpressure to a low pressure at a faster rate. The valves 13 and 14, byperiodically opening and closing, allow the variable pressure producedby this pump to be varied as it is exerted on the column of powertransmission fluid in area 33. The two valves l and i4 may be poweroperated; the power to operate them can be obtained by connecting a lineto the gas outlet conduit of the unit 22.

The system described herein will operate most eticiently when thecompressibility of the power transmission lluid is low. In order tominimize the horse power requirements for pump lli it is desirable butnot essential to use a power transmission uid having a greater densitythan that of the well efiluent being handled. For example, if the welleffluent is oil, a salt water solu tion or dead oil would work well andwould normally be available at the average field.

The two check valves 3l and 32 may be of a conventional type. Apreferable construction of the valves 27 and 36 (without their checkmechanisms) is shown in FIG. 5 and of the valves 23 and 29 (withouttheir check mechanisms) is shown in FIG. 6. If desired, the valves 27-32may be provided with means whereby they can be retrieved by variousmeans such as wire line methods.

The valve shown in FIG. 5 is a dual bellows type that is designed toopen at a rst pressure and close at a second higher pressure. Itincludes a fishing neck 50 at its uppermost end which is connected to abellows carriage 5l. Within this carriage 51 is a bellows 52 and aflexible inner liner 53 which forms a bellows chamber 54. This bellowschamber is initially charged to a predetermined pressure, for example,by removing the shing neck 5t) `and charging the chamber through a portformed in the bellows carriage.

A bellows base 55 and a valve stern 56 are attached to the bellows 52.An optional adjusting nut 57 is threaded onto the valve stem 56 and anoptional compression spring 58 may be disposed between this adjustingnut and a block 59 that is formed on the carriage 51 of the valve. Theforce produced by this compression spring, which supplements the forceproduced by the bellows 52 and absorbs shock loads, can be adjusted bysetting the position of the adjusting nut 57. It should also be notedthat other embodiments are envisioned which use tension springs andarrangements which result in reducing the force exerted by the bellowsto the predetermined value or arrangements which replace the `bellowsentirely. Also fastened tto the valve stem 56 is an upper valve member61 which is `seated in an upper valve seat 62 that forms part of thecasing 6l) for this valve.

The lower portion of this valve is somewhat similar to the end justdescribed. The lower end of this valve is equipped with a cap 63 whichmay be removed prior to charging a lower bellows` chamber 64. A bellowsbase 75 and a valve stem 76 are attached toa bellows 72. In a similarmanner as described above an optional adjusting nut 77 is -threaded ontoa valve stem 76 and an optional compression spring 78 may be disposedbetween this adjusting nut and block 79. A lower valve member 65 isfastened to the valve stem 76 and is adapted to be received in a lowervalve seat 66. It should be noted that the normal position for the valvemember 65, when the system is below its predetermined closing pressure,is located above the valve seat 66 so that the passage at this point isopen.

The upper portion of the valve case 60 has a port 67 formed thereinwhich, when this valve is being used as the valve 27 in the pump, is incommunication with the chamber 36 in the pump. The mid-portion of thevalve case 60 has a port 68 which is connected to the casing area 33.The port 65 is formed in the same general casing that forms the valveseats 62 and 66,

When this valve is to be used as the valve 27 in the pump 19, theposition of the valve members 6l and 65' is adjusted on the valve stems56 and 76 so that upper valve member 6l is seated tightly in valve seat62 and, as stated above, valve 65 is initially open when the pres* surebeing exerted by the pump lil at the surface of the ground is below apredetermined level which is higher than the opening pressure of valvemember 61. The flow of power transmission lluid through the port 68 andout of the port 67 is, therefore, cut oil at this position ofequilibrium.

When the pressure on the power transmission fluid is increased to thepoint indicated on FIG. 4 as the opening pressure for the valve 27, theupward force of :sn-saaie the power transmission fluid acting throughthe port 63 against the under surface of the valve 6l overcomes theresistive force of bellows S2 and the compression spring 53, and causesthe valve member 6l to move of valve seat 62, so that the powertransmission fluid is able to llow through the valve and out of the port67.

As `stated above, once valves 27 and 3@ open, the pressure exerted bythe power transmission fluid continues to increase but at a lesser rater-Sll as shown in FG. 4 as the traveling barrel 26 moves upwardly. Whenthe force resulting from this pressure on this valve, when used as valve27, is equivalent to and exceeds the pressure and resulting force towhich the lower bellows chamber 64 is pre-charged, which is the closingpressure for this valve, the pressure of power transmission liuid on theupper surface of valve member 65 overcomes the fluid pressure on thelower surface of said valve, the force of the bellows 72, and the forceof the compression spring 78. This downward resultant force causes thevalve member 65 and the valve stem 75 to descend. This downward movementcontinues until valve member 65 rests tightly against valve seat 66thereby discontinuing the ow of power transmission duid through thisvalve.

When the pressure applied by surface pump l@ is decreased to the pointwhere the force applied is less than the internal force in the lowerbellows chamber 64, and its supplemental forces, the valve member 65once again opens as valve stem 76 and moves upwardly and away from valveseat 66. As the pressure applied by the surface pump continues torapidly decrease, the upper bellows S2 expands and returns the valvemember 6l to its normally closed position.

Packing elements 69a, 69h and 69e are provided on the sides of the valvecasing so that the valve can be properly received in a mandrel providedin the pump 19. These packing elements also serve to isolate the variousports in the valve from each other. internal packing elements 79a and7M, in turn, isolate the upper and lower bellows from the fluid flowchambers.

When the valve in FIG. 5 is used as valve 3l? in pump 19, it functionsin a manner identical to that described for the valve 27 except that thepassageway is in cornrmunication with the power transmission fluid inthe chamber 42 instead of the casing area 33 as it was in valve 27. Theport 67 is in communication with the channel 4l in valve 3h instead ofthe chamber 36 as it was when usedinvalve 27.

The valve shown in PEG. 6 is a single bellows type. Althoughstructurally unique this valve encompasses virtually the same principlesas those disclosed by the upper portion of the valve shown in FlG. 5. Itincludes a removable fishing neck titl at its uppermost end throughwhich bellows chamber 8e is initially charged to a predeterminedpressure. A bellows base 5S and a valve stem 86 are likewise attached tothe bellows 82. Also an optional compression spring 83 may be disposedbetween optional adjusting nut 3l and a block 89 that is formed on thecarriage of the valve. The force of this compression spring supplementsthe force produced by the bellows 82 and may optionally replace it. Whenthe pressure of the power transmission lluid acting through inlet port88 reaches sufficient magnitude, valve 9i, located at the lowermostpoint of valve `stem de, is forced from valve seat 92, thereby allowingliuid to flow through the valve and out through outlet port S7.

When this valve is used as the valve Zh, port Sie is connected to thecasing area 33 and the outlet port S7 is connected to the chamber ft2.When it is used as the valve 2S the inlet port is communicated with thechamber 36 and the outlet port 57 is connected to channel Again packingelements 69a, 69h and 69e are provided on the sides of the valve casingthereby serving to isolate the Various valve ports from each other.internal packing elements 7l isolate the bellows 82 from the fluid flowchambers.

FlGS. 7 through 9 disclose a more detailed and specifically operationaldesign in which the positions of the valve mandrels and the pumps tubingare shown.

Fthe outline of valve 27 is shown positioned and locked in its receiver97 by locking device lll. Mandrel 97 is an integral part of pump section19C which is the lower portion of pump 19. Entrance port 68 of valve 27is effectively sealed in communication with casing area 33 by virtue ofpacking elements 69a and 6911 as shown in FlG. 5, being sealed inpacking areas lll and lZ as shown in PEG. 7. Outlet port 67 is similarlysealed in mandrel 97 in communication with chamber or channel 36 byvirtue of packing seals 69h and 69e being seated in areas lll) and M3respectively.

Valve 23 is positioned and locked in its receiver 98 by its lockingdevice lili. Inlet port 8S of valve 28 is sealed in communication withchamber 36 by its packing elements 69a and 6% (FIG. 6) sealing in areaslll and M5 respectively. Outlet port 87 is sealed in communication withchannel 39 by packing elements 69h and 69C being sealed against areasllS and M6 (FlG. 7), respectively.

So positioned, valves 27 and 28 function in the manner previouslydescribed. FIGS. 7A through 7D illustrate various cross-sectional areasof the general construction arrangements of section i90.

Section 19C is connected to section 19h (FIG. 8) of pump 19 by athreaded connection. The conduit channels 36 and 39 just described areconnected to a continuation of these channels in FIG. 8. Appropriateseals 73a (FIGS. 7 and 8) maintain communication between con-duitsections of channels 36 and 39. Allen head screws or comparable lw-(FiGS. 7 and 8) hold the conduit channels 36 and 35 in permanentposition.

FIG. S shows the central section of pump i9 including traveling barrel26. r,This detailed configuration is basically the saine as the first,although certain structural changes make it more streamlined andcompact. It is noted that in FIG. 8 members T17 and 24, as shown inFIGS. 2 and 3, are in intimate contact. lt is further noted that sealingelements 48 previously shown on either side of member d3 (FGS. 2 and 3)may be designed as single sealing elements flon the internal side ofmember 43 (FlG. 8). It is recognized, however, that in other embodimentsnot shown the internal member 38 of barrel 26 may be omitted and seals48 may be located on the external member 33 of barrel 26 to effect aseal on the external side of cylindrical member 43.

ln FIG. 8, check valve 3l, located in the bottom plate of travelingbarrel 25, is shown nearing the top or the half-way point in itsdisplacement cycle. This valve is locked in position to the bottom plateof traveling barrel 2e by locking device lll2.

Hydraulic brakes 93a-91la and @3b-Mb, illustrated in FIG. 8, aremechanisms to Control the upper and lower stroke limits of the travelin7 barrel 26. The hydraulic brake is composed of an accurately machinedmember 53 that is essentially a free iloating member within its confinedarea and a ball-seat check valve 94. This check valve may be either amagnetic or gravity type. I As traveling barrel 26 approaches its upperlimit durlng its displacement cycle, the upper end of exterior member 38contacts free floating member 93a. The continued upward movement ofmember 33 forces member 93a upward until it contacts the ball 94a andforces it olf the seat. When this occurs, area 42 is then incommunication with casing area 33. With the pressure in chamber 4Z equalto the pressure in chamber 36, no resulting force is imparted totraveling barrel 26 and the friction of the system soon halts theremaining upward inertia. A similar braking effect occurs on thedownstroke of traveling barrel 26 as the lower end of member 33 contactsthe free floating member @3b.

All other operational functions of the various members within section19h (FIG. 8) are the same as has been previously described for thegeneral configuration shown in FIGS. 2 and 3.

The upper extremity of section 19h of pump 19 becomes an integralportion of section 19a by threaded connections. The channels 42 and 39of member 19h are connected t the same channels in section 19a. Allenhead type locking screws 195 lock the conduit connections of channels 42and 39 together. Sealed communications of these channels are effected byseals 7317 (FIG. 9).

ln FIG. 9 dotted lines indicate the operating position of valve 29 inits receiving chamber 99. Entrance port 88 is isolated in communicationwith casing area 33 as a result -of packing seals 69a and 69h (FlG. 6)being seated in packing areas 117 and 118 (FIG. 9), respectively. Theexit port S7 of valve 29 is sealed and in communication channel 42 as aresult of seals 69h and 69C (FIG. 6) being seated in areas 118 and 119(FlG. 9). Valve 29 is locked into position by its latching device 101.

The outline of valve 30 (FIG. 5) is indicated in its operating positionin its receiving chamber 109 in FIG. 9. The entrance 68 is isolated incommunication with channel 42 as a result of seals 69a and 69b (FIG. 5)being seated in areas 120 and 121 (FiG. 9) respectively. Exit port 67(FIG. 5) is isolated in communication with channel 41 and productiontubing 2li as a result of seals 69b and 69C being seated in areas 121and 122 in FIG. 9. Valve 30 is locked in this position by its latchingdevice 101.

So positioned valves 29 and 30 function in the manner described in thefirst general configuration.

In FIG. 9 the check valve 32 is located in the stationary upper plateforming the top of barrel 26 and is locked in position by locking device103.

The FIGS. 9A through 9D illustrate the general construction of section19a more clearly.

The fishing necks 50 (valves 27 and Sil), 8u (valves 28 and 29), 108(check valve 31) and 109 (check valve 32) are to accommodate Itheplacing and retrieving of these valves by portable wire line equipmentwhen the tubing is not to be removed from the hole. The various latchingand locking devices lill-103 are so designed that an upward or downwardforce applied to the fishing necks by the running and retrieving toolsresults in unlocking or locking lthe various valves with respect totheir mandrels. It is recognized and considered as a portion of thisinvention that the valves 27 32 may t the position permanently withinthe body of the overall pump 19 and that the complete pump may beretrieved by either wire, line, pipe, sucker rod or hydraulictechniques.

While representative embodiments of the present invention have beenshown and described for the purposes of illustration, it is apparentthat the embodiments are susceptible of change and modification withoutdeparting from this invention in its broader aspects. For example, whilethe specifically disclosed exemplary embodiments illustrate the liftingof fluids from a subterranean location, the disclosed system of theinvention is obviously applicable to the movement of fluids bothvertically and horizontally in a wide variety of fluid transmissionconduits on, above or below the surface of the earth or through land orwater formations thereof.

The fluid supply and pressure relief functions of the valve manifoldincluding the valves 13, 14 and 15 may be provided by a wide variety ofother suitable valve manifold arrangements. Further, the valve structureshown in FIGS. and 6 will have many other applications in fluid systems.Therefore, the invention described herein is not to be construed aslimited to the specific embodiments described but is intended toencompass all modifications thereof coming within the scope of thefollowing claims.

I claim:

l. A system for obtaining fluids from distant locations comprising afluid pumping mechanism adapted to be disposed at a first distantlocation, a source of power transmission fluid adapted to be disposed ata second accessible location, conduit means connecting said source tosaid pumping mechanism, means for periodically applying variablepressure on the power transmission fluid contained in said -conduitmeans, a movable member contained in said pumping mechanism fordisplacing fluid, first pressure responsive valve means `coupled to saidpumping mechanism which is adapted to enable the power transmissionfluid to exert a force in a first direction on said movable member whensaid pressure is at a first magnitude, and second pressure responsivevalve means coupled to said pumping mechanism which is adapted to enablethe power transmission fluid to exert a yforce in a second direction onsaid movable member when said pressure is at a second higher magnitude.

2. A system for obtaining fluids from distant locations of the `typedescribed in claim l wherein said means for periodically applyingpressure on the power transmission fluid contained in said conduit meansincludes a fluid pump coupled to deliver fluid under pressure to saidconduit means, and valve means coupled to said conduit means betweensaid fluid pump and said pumping mechanism which is adapted to open andclose to the flow of the power transmission fiuid in said conduit.

3. A system for obtaining fluids from distant locations of the typedescribed in claim 1 wherein said means for periodically applyingpressure on the power transmission fluid contained in said conduit meansincludes a fluid pump coupled to deliver fluid under pressure to saidconduit means, third pressure responsive valve means coupled to saidconduit which is adapted to periodically permit the flow of said powertransmission fluid through said conduit, a return conduit coupled tosaid third valve means in such a manner as to receive said powertransmission fluid when said third valve means does not permit fluidflow through said conduit means, and a reservoir coupled to receivefluid from said return line and supply it to said fluid pump.

4. A system for obtaining fluids from distant locations of the typedescribed in claim l wherein said movable member includes a hollowelongated member having means lat a first end through which fluids canenter and means at its opposite end through which fluids can leave, andguide means for guiding the movement of said movable member.

5. A pumping mechanism for obtaining fluids from distant locationscomprising a movable member adapted to be disposed at a distantlocation, guide means attached to said movable member for guiding itsmovement, first valve means coupled to said movable member which enablesfluid to enter said member, second valve means which enables fluid toleave said pumping mechanism, third valve means for enabling powertransmission fluid to pass therethrough and exert a force in onedirection on said movable member when the pressure of the fluid is at afirst magnitude, and fourth valve means for enabling power transmissionfluid to flow therethrough and exert a force in an opposite direction onsaid movable member when the pressure of the fluid is at a second highermagnitude.

6. A pumping mechanism of the type described in claim 5 and furtherincluding fifth valve means to enable a quantity of the powertransmission fluid to flow therethrough as it is displaced when saidmovable member is forced in said one direction, and sixth valve means toenable a quantity of said power transmission fluid to ilow therethroughas it is displaced when said movable member is forced in said oppositedirection.

7. A pumping mechanism for obtaining fluids from distant locationscomprising a member that is movable between a first position and asecond position, guide means for guiding the movement of said memberbetween said first and second positions, a first pressure responsivevalve andere for passing a power transmission fluid therethrough whenthe pressure on the fluid is at a first magnitude, a second pressureresponsive valve'for passing a power transmission fluid therethroughwhen the pressure on the fluid is at a second higher magnitude, themember being constructed such that the power transmission fluid passingthrough the first valve forces the member to move from the firstposition to the second position and the power transmission fluid passingthrough the second valve forces the member to move from the secondposition to the first position, a third pressure responsive valve toenable a quantity of the power transmission fluid to flow therethroughwhen it is displaced by said movable member moving toward said secondposition, a fourth pressure responsive valve to enable a quantity of thepower transmission fluid to flow therethrough when it is displaced bysaid movable member moving toward said first position, first check valvemeans mounted on said movable member which allows a fluid to flowtherethrough and fill said movable member as said member moves towardsaid first position, and second check valve means which allows the fluidto pass therethrough out of said movable member as said member movestoward said second position.

8. A pumping mechanism of the type described in claim 7 wherein thefirst, second, third and fourth pressure responsive valves each operatein combination with a one-way check valve.

9. A pumping mechanism of the type described in claim 7 wherein said rstand third pressure responsive valves each comprise an elongated hollowcasing, a plurality of valve stems mounted lengthwise of the casing, abellows fastened to one end of each valve stem, each of said bellowsbeing adapted to be initially charged to a predetermined pressure, valvemembers mounted on each valve stem and mating valve seats mounted onsaid casing, a fluid channel between two ports formed through saidpressure valve along a path that includes said valve members and saidvalve seats, one of said valve members being positioned in its saidmating valve seat such that it allows uid to flow through said channelwhen the fluid pressure at one of said ports is greater than apredetermined value, and another of said valve members being positionedabove its said mating valve seat such that it allows fluid to flowthrough said channel until the fluid pressure at one of said portsexceeds a second higher predetermined value.

10. A pumping mechanism with pressure responsive valves as described inclaim 9 wherein a spring is mounted on at least one of said valve stemsfor changing the pressure exerted by said bellows.

11. A pumping mechanism with pressure responsive Valves as described inclaim 9 wherein seals separate the said bellows from the said fluidchannel.

12. A pumping mechanism with pressure responsive valves as described inclaim 1() wherein seals separate the said bellows and said spring fromthe said fluid channel.

13. A pumping mechanism of the type described in claim 7 wherein saidsecond and fourth responsive valve means each comprise a hollow casing,a valve stem mounted lengthwise of the casing, a bellows fastened to oneend of said valve stem, said bellows being adapted to be initiallycharged to a. predetermined pressure, a valve member mounted on saidvalve stem and a mating valve seat mounted on said casing, a fluidchannel between two ports formed through said pressure valve along apath that includes said valve member and said valve seat, said valvemember being positioned in said valve seat such that it allows fluid toflow through said channel when the fluid pressure at one of said portsis greater than a predetermined value.

14. A pumping mechanism with pressure responsive valves as described inclaim 13 wherein a spring is mounted on said valve stem for changing thepressure exerted by said bellows.

15. A pumping mechanism with pressure responsive valves as described inclaim 13 wherein seals separate the said bellows from the said fluidchannel.

16. A pumping mechanism with pressure responsive valves as described inclaim 14 wherein seals separate the said bellows and said spring fromthe said fluid channel.

17. A pumping mechanism of the type described in claim 7 wherein saidpressure responsive valves include means for securing said valves inreceiving mandrels and for facilitating retrieval therefrom.

18. A pumping mechanism of the type described in claim 7 wherein saidinlet and outlet fluid check valves include means for securing saidvalves and for facilitating retrieval.

19. A pumping mechanism of the type described in claim 7 wherein brakingmeans equalize the pressure on each side of the said movable member whenit nears upper or lower limits, thereby stopping said movable member.

20. A pumping mechanism responsive 4to periodic increases and decreasesin a power transmission fluid for obtaining fluids from distantlocations comprising a pumping member that is movable between a firstposition and a second position for displacing the fluid to be pumped,guide means for guiding the movement of said member between said rst andsecond positions, said pumping member having first and second opposingpressure responsive control surfaces adapted to be selectively incommunication with the power transmission fluid for urging said membertoward a respective one of said first and second positions, a firstpressure responsive valve for passing power transmission fluidtherethrough when the pressure of said power transmission fluid is at afirst magnitude to place said first opposing surface in freecommunication with said power transmission fluid to urge said memberfrom said irst position toward said second position, a second pressureresponsive valve for passing power transmission fluid therethrough whenthe pressure of said power transmission fluid is at a second highermagnitude to place said second opposing surface in free communicationwith said power transmission fluid to urge said member from said secondposition toward said first position, a third pressure responsive valvefor enabling said power transmission fluid in communication with saidsecond opposing surface to be relieved when said power transmission uidis displaced by said movable member moving from said first positiontoward said second position, a fourth pressure responsive valve forenabling said power transmission fluid in communication with said firstopposing surface to be relieved when said power transmission fluid isdisplaced by said movable member moving from said second position towardsaid first position.

21. A pumping mechanism as described in claim 2() wherein braking meansare provided for stopping said movable member on reaching said first andsecond positions, said braking means comprising Valve means forselectively placing each of said opposed surfaces in free communicationwith said power transmission fluid, and actuating means responsive tothe position of said movable member as it approaches said first andsecond positions for operating said respective valve means to equalizethe pressure of power transmission fluid on said opposing surfaces.

References Cited in the file of this patent UNTED STATES PATENTS2,624,285 Hall Jan. 6, 1953 2,628,565 Richardson Feb. 17, 1953 2,780,171Heddy Feb. 5, 1957 2,870,749 Deitrickson Jan. 27, 1959 2,884,952 Masonet al. May 5, 1959 2,890,715 Ebersold June 16, 1959 2,984,224 Brennan etal May 16, 1961

1. A SYSTEM FOR OBTAINING FLUIDS FROM DISTANT LOCATIONS COMPRISING AFLUID PUMPING MECHANISM ADAPTED TO BE DISPOSED AT A FIRST DISTANTLOCATION, A SOURCE OF POWER TRANSMISSION FLUID ADAPTED TO BE DISPOSED ATA SECOND ACCESSIBLE LOCATION, CONDUIT MEANS CONNECTING SAID SOURCE TOSAID PUMPING MECHANISM, MEANS FOR PERIODICALLY APPLYING VARIABLEPRESSURE ON THE POWER TRANSMISSION FLUID CONTAINED IN SAID CONDUITMEANS, A MOVABLE MEMBER CONTAINED IN SAID PUMPING MECHANSM FORDISPLACING FLUID, FIRST PRESSURE RESPONSIVE VALVE MEANS COUPLED TO SAIDPUMPING MECHANISM WHICH IS ADAPTED TO ENABLE THE POWER TRANSMISSIONFLUID TO EXERT A FORCE IN A FIRST DIRECTION ON SAID MOVABLE MEMBER WHENSAID PRESSURE IS AT A FIRST MAGNITUDE AND SECOND PRESSURE RESPONSIVEVALVE MEANS COUPLED TO SAID PUMPING MECHANISM WHICH IS ADAPTED TO ENABLETHE POWER TRANSMISSION FLUID TO EXERT A FORCE IN A SECOND DIRECTION ONSAID MOVABLE MEMBER WHEN SAID PRESSURE IS AT A SECOND HIGHER MAGNITUDE.